EP1790926A1 - Procédé et dispositif de refroidissement d'un courant, en particulier d'un courant d'hydrocarbures comme du gaz naturel - Google Patents

Procédé et dispositif de refroidissement d'un courant, en particulier d'un courant d'hydrocarbures comme du gaz naturel Download PDF

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Publication number
EP1790926A1
EP1790926A1 EP06124522A EP06124522A EP1790926A1 EP 1790926 A1 EP1790926 A1 EP 1790926A1 EP 06124522 A EP06124522 A EP 06124522A EP 06124522 A EP06124522 A EP 06124522A EP 1790926 A1 EP1790926 A1 EP 1790926A1
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EP
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Prior art keywords
refrigerant fluid
compressed
stream
refrigerant
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06124522A
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German (de)
English (en)
Inventor
Marco Dick SHELL GLOBAL SOLUTIONS Jager
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Shell Internationale Research Maatschappij BV
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Shell Internationale Research Maatschappij BV
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Publication of EP1790926A1 publication Critical patent/EP1790926A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0022—Hydrocarbons, e.g. natural gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/0052—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0294—Multiple compressor casings/strings in parallel, e.g. split arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/13—Economisers

Definitions

  • the present invention relates to a method and apparatus for cooling a stream, in particular a hydrocarbon stream such as natural gas.
  • the present invention relates to a compressor arrangement and in particular to the use thereof in a refrigerant circuit for use in a method and apparatus for producing a liquefied stream such as a liquefied hydrocarbon stream such as a liquefied natural gas (LNG) stream.
  • a liquefied stream such as a liquefied hydrocarbon stream such as a liquefied natural gas (LNG) stream.
  • LNG liquefied natural gas
  • the refrigerant is successively compressed in a compressor arrangement, cooled against e.g. water or air in a first heat exchanger, expanded and evaporated in a second heat exchanger (usually a cryogenic heat exchanger) where the refrigerant cools at least the natural gas stream to be cooled.
  • a second heat exchanger usually a cryogenic heat exchanger
  • US 5 826 444 An example of a known method for cooling a hydrocarbon stream is disclosed in US 5 826 444 .
  • US 5 826 444 relates to a process and to a device allowing to liquefy a fluid or a gaseous mixture consisting at least partly of a mixture of hydrocarbons, for example natural gas.
  • the compressor arrangement used for compressing the refrigerant in the known refrigerant circuits usually comprises only one or more centrifugal compressors and no axial compressors, due to the fixed optimal pressure ratio of an axial compressor.
  • One or more of the above or other objects are achieved according to the present invention by providing a method of cooling a stream, in particular a hydrocarbon stream such as natural gas, wherein a stream is cooled in a heat exchanger against a refrigerant fluid being cycled in a refrigerant circuit, the cycling of the refrigerant fluid at least comprising:
  • the present invention makes use of a surprisingly simple and flexible compressor arrangement containing a specific combination of an axial and a centrifugal compressor.
  • An important advantage of the present invention is that - despite the presence of the axial compressor - a refrigerant fluid being composed of streams having different pressure levels and being cycled in a refrigerant circuit can be handled during compression in a surprisingly simple and efficient manner. This is in particular advantageous if a mixed refrigerant is used in the refrigerant circuit with multiple cryogenic heat exchangers.
  • a further advantage of the compressor arrangement used in the method according to the present invention, wherein an axial compressor is arranged partially parallel to a centrifugal compressor, is that a pressure ratio of about 6 across the axial compressor can be maintained while at the same time the compressor arrangement can handle various stream having different pressure levels.
  • Another advantage of the compressor arrangement used in the method according to the present invention is that a lower specific power is needed than if a single centrifugal compressor or two centrifugal compressors in series would be used.
  • An even further advantage of the present invention is that by use of the axial compressor the volumetric flow in any point of the centrifugal compressor in the compressor arrangement is significantly lowered.
  • the stream to be cooled may have various compositions, but is preferably a hydrocarbon stream.
  • the hydrocarbon stream may be any hydrocarbon-containing stream to be cooled, but is usually a natural gas stream obtained from natural gas or petroleum reservoirs.
  • the natural gas stream may also be obtained from another source, also including a synthetic source such as a Fischer-Tropsch process.
  • a natural gas stream is comprised substantially of methane.
  • the natural gas comprises at least 60 mol% methane, more preferably at least 80 mol% methane.
  • the natural gas may contain varying amounts of hydrocarbons heavier than methane such as ethane, propane, butanes and pentanes as well as some aromatic hydrocarbons.
  • the natural gas stream may also contain non-hydrocarbons such as H 2 O, N 2 , CO 2 , H 2 S and other sulphur compounds, and the like.
  • the natural gas stream may have been pre-treated before cooling. This pre-treatment may comprise removal of undesired components such as H 2 O, CO 2 and H 2 S, or other steps such as pre-cooling, pre-pressurizing or the like. As these steps are well known to the person skilled in the art, they are not further discussed here.
  • the refrigerant fluid being cycled in the refrigerant circuit may be a single component refrigerant or a mixed refrigerant containing several compounds having different boiling points.
  • the refrigerant fluid will usually be selected from one or more of the group consisting of nitrogen; lower hydrocarbons such as methane, ethane, ethylene, propane, propylene, butane, pentane; or mixtures thereof thereby forming a mixed refrigerant.
  • a mixed refrigerant is used as the refrigerant fluid.
  • the first and second refrigerant fluids being fed in steps (a) and (d) are not limited to a specific composition. They may contain different components or different mixtures of components or they may be parts of the refrigerant stream having the same composition.
  • the heat exchanger in which the natural gas stream is cooled may be a single heat exchanger or a heat exchanger train comprising two or more heat exchangers or heat exchanging zones, as long as the at least two streams obtained in step (g) can be evaporated at different pressure levels.
  • the separation of the cooled compressed refrigerant fluid mixture in step (g) may be performed in various ways, also depending on whether a single component refrigerant or a mixed refrigerant is used as the refrigerant fluid being cycled in the refrigerant circuit. If a mixed refrigerant is used, e.g. a T-junction may be used. If a single component is used, the separation may take place while the cooled compressed refrigerant fluid mixture obtained in step (f) passes through the heat exchanger or a zone thereof intended for cooling the natural gas stream in step (h). In the latter case, a part of the single component evaporates at a higher pressure level, while the remainder is passed to a lower pressure zone of the same or other heat exchanger and is evaporated there.
  • the present invention provides an apparatus for cooling a stream, in particular a hydrocarbon stream such as natural gas, optionally producing a liquefied natural gas stream, wherein the stream is cooled in a heat exchanger against a refrigerant fluid being cycled in a refrigerant circuit, the refrigerant circuit at least comprising:
  • the separator comprises a T-junction, in particular if a mixed refrigerant is the refrigerant fluid being cycled in the refrigerant circuit.
  • the present invention provides a refrigerant circuit as described in the apparatus according to the present invention and the use thereof for cooling a stream, in particular natural gas.
  • the present invention provides a compressor arrangement as described in the apparatus according to the present invention, the compressor arrangement comprising:
  • the refrigerant circuit and compressor arrangement according to the present invention are not only suitable (and preferably intended) for cooling a natural gas stream, but may be used for any fluid to be cooled.
  • Figure 1 schematically shows the apparatus 1 according to the present invention for liquefying a natural gas stream 10 using a mixed refrigerant being cycled in a refrigerant circuit 3.
  • the mixed refrigerant suitably comprises a mixture of two or more of nitrogen, methane, ethane, propane and butane.
  • a mixed refrigerant is used as the refrigerant fluid
  • a single component refrigerant such as propane may be used instead.
  • the apparatus 1 comprises a heat exchanger train 2 comprising two or more heat exchangers (or heat exchanging zones) 2a and 2b, in which the natural gas stream 10 is cooled against a refrigerant being cycled in a refrigerant circuit 3. After cooling in the heat exchanger train 2, a cooled natural gas stream (which may be partly liquefied) 100 is obtained.
  • the apparatus may comprise more heat exchangers thereby cooling the natural gas stream 10 in several steps into liquefaction.
  • the apparatus 1 may comprise a pre-cooling system with a pre-cooling refrigerant circuit, a main cryogenic system with a main refrigerant circuit and a sub-cooling system with a sub-cooling refrigerant circuit.
  • a pre-cooling system with a pre-cooling refrigerant circuit a main cryogenic system with a main refrigerant circuit
  • a sub-cooling system with a sub-cooling refrigerant circuit for reasons of simplicity, only one cooling system with one refrigerant cycle has been shown in Figure 1.
  • the natural gas stream 10 may have been pre-treated, e.g. to remove any undesired components such as H 2 O, CO 2 , sulphur compounds such as H 2 S, and the like.
  • the refrigerant circuit 3 comprises a specific compressor arrangement 4 being composed of an axial compressor 5 and a centrifugal compressor 6. If desired, the compressor arrangement 4 may comprise more than two compressors.
  • the axial compressor 5 has an inlet 7 for a first refrigerant fluid 20 to be compressed and an outlet 8 for a compressed first refrigerant fluid 30.
  • the centrifugal compressor 6 has a first inlet 9 for the compressed first refrigerant fluid 30 that has been compressed in the axial compressor 5 and a second inlet 11 for a second refrigerant fluid 40. If desired, stream 30 leaving the outlet 8 of the axial compressor 5 may be intermediately cooled against another stream (not shown) before passing to the inlet 9 of centrifugal compressor 6.
  • the compressed first refrigerant fluid 30 and the second refrigerant fluid 40 are concurrently compressed in the centrifugal compressor 5 thereby obtaining a compressed refrigerant fluid mixture 50 being removed from outlet 12.
  • the refrigerant circuit 3 comprises a heat exchanger 13 for cooling the compressed refrigerant fluid mixture 50 (which is fed via inlet 18) against a cooler stream, thereby obtaining a cooled compressed refrigerant fluid mixture 60 (which is removed via outlet 19).
  • the heat exchanger 13 may be an air or water cooler, wherein air or water functions as the coolant.
  • the outlet 19 of the heat exchanger 13, in which the compressed refrigerant fluid mixture 50 has been cooled, is connected via line 60 to the first inlet 21a of the cold side 17a of the natural gas cooling heat exchanger 2a.
  • the apparatus 1 comprises a separator 33 for separating the cooled compressed refrigerant fluid mixture 65 into at least two streams.
  • the separator 33 comprises a T-junction to obtain the at least two streams to be evaporated in the heat exchanger train 2.
  • the separator 33 is placed between the first outlet 31a of the heat exchanger 2a (to be further discussed hereinafter) and the first inlet 21b of the heat exchanger 2b.
  • One of the two streams is passed (as stream 70) to expander 45a, while the other stream (stream 80) is passed to the first inlet 21b of the heat exchanger 2b and subsequently passed (via line 110b) to first outlet 31b and expander 45b.
  • the separator 33 may be placed on an other suitable location as long as at least two streams are obtained that can be evaporated in the heat exchanger train 2 at different pressure levels.
  • the separator 33 is placed somewhere between the first outlet 31a of the heat exchanger 2a and the first inlet 21b of the heat exchanger 2b.
  • the cooled compressed refrigerant fluid mixture 65 may be split into more than two streams, if desired.
  • the two streams 70,80 obtained as described above are evaporated at different locations and at different pressure levels in the heat exchanger train 2 thereby cooling the natural gas stream 10.
  • one of the above two streams is evaporated in heat exchanger 2a, while the other one is evaporated in heat exchanger 2b, wherein the stream being evaporated in heat exchanger 2a is evaporated at a higher pressure and temperature than the stream being evaporated in heat exchanger 2b.
  • the heat exchanger train 2 comprises further heat exchangers 2c, 2d, etc, the temperature and pressure at which the respective streams are evaporated preferably will decrease, going from heat exchanger 2a to 2b to 2c, etc.
  • the natural gas cooling heat exchangers 2a,2b have a hot side schematically shown in the form of tubes 14a,14b having inlets 15a, 15b for natural gas 10 and outlets 16a,16b for cooled natural gas.
  • the tubes 14a,14b are arranged in the cold side 17a, 17b, which can be a shell side of the natural gas cooling heat exchangers 2a,2b.
  • the outlet 16a of heat exchanger 2a is connected via line 75 to inlet 15b of heat exchanger 2b.
  • the heat exchangers 2a,2b also comprise conduits 110a,110b for transporting the respective refrigerant streams through the respective heat exchanger, from the first inlets 21a,21b to the first outlets 31a,31b.
  • the stream 65 removed from the first outlets 31a is split in separator 33 into the streams 70 and 80.
  • Stream 80 is passed to the first inlet 21b of the heat exchanger 2b, whilst stream 70 is expanded in expander 45a and returned (as stream 90) via second inlet 27a into the heat exchanger 2a in which it is evaporated.
  • the evaporated stream is collected at second outlet 22a at the bottom of the heat exchanger 22a.
  • the stream 80 is fed at first inlet 21b into heat exchanger 2b, passed through the heat exchanger as stream 110b and removed from the heat exchanger 2b at the first outlet 31b as stream 85. Subsequently, stream 85 is expanded in expander 45b and returned via line 95 at second inlet 27b into the heat exchanger 2b in which it is evaporated. The evaporated stream is collected at second outlet 22b near the bottom of the heat exchanger 2b.
  • the stream 85 removed from outlet 31b of heat exchanger 2b may be further split in a suitable manner.
  • One of the streams obtained then would be used as a feed to the expander 45b, whilst (one of) the other stream(s) could be used as a feed for the heat exchanger 2c.
  • the second outlet 22 of the cold side 17a is connected by means of return conduit 40 to the second inlet 11 of the centrifugal compressor 6.
  • the second outlet 22b of the cold side 17b is connected by means of return conduit 20 to the inlet 7 of axial compressor 5.
  • knock out drums (not shown) are present in the lines 20,40 to prevent that liquid is fed into the compressors 5,6.
  • natural gas 10 is supplied to the cooling heat exchanger train 2, is stepwise cooled in heat exchangers 2a,2b against the refrigerant being cycled in the circuit 3 as described above, and is removed as a cooled fluid 100 from the heat exchanger 2b at outlet 16b.
  • the second refrigerant fluid 40 has a higher pressure than the first refrigerant fluid 20.
  • the first refrigerant fluid 20 is fed into the axial compressor 5 at a pressure in the range of 2-5 bar, preferably about 3 bar.
  • the compressed first refrigerant fluid 30 is fed into the centrifugal compressor 6 at a pressure in the range of 12-30 bar. It is even more preferred that the pressure of the compressed first refrigerant fluid 30 that is fed into the centrifugal compressor 6 is five to seven times as high as the pressure of the first refrigerant fluid 20 that is fed into the axial compressor 5, preferably about 6 times as high.
  • the second refrigerant fluid 40 is fed into the centrifugal compressor 6 at a pressure in the range of 6-15 bar and that the compressed refrigerant fluid mixture 50 has a pressure in the range of 25-60 bar. Furthermore the compressed first refrigerant fluid 30 is at a higher pressure than the second refrigerant fluid 40.
  • the temperature at the first inlet 21a of heat exchanger 2a will generally be in the range of from 50 to -50 °C; the temperature at the first outlet 31a of heat exchanger 2a will be in the range of from 20 to -80 °C. Further, the temperature at the first inlet 21b of heat exchanger 2b will generally be in the range of from 20 to -80 °C; the temperature at the first outlet 31b of heat exchanger 2b will be in the range of from 0 to -110°C.
  • Figure 2 shows schematically the compressor arrangement 4 according to the present invention
  • Figure 3 shows a compressor arrangement wherein an axial compressor and a centrifugal compressor are placed in series.
  • the refrigerant stream being compressed in the compressor arrangement of Figure 3 must have a single pressure.
  • the arrangement according to Figure 3 is - contrary to the arrangement 4 according to the present invention as shown in Figure 2 - not suitable for compressing a refrigerant stream that is composed from different streams having different pressures.
  • Table 1 shows the temperature, pressure, flow rate and phase condition of the various natural gas streams in a simulated example, whilst Table 2 shows the same for the various streams within the refrigerant cycle.
  • stream 60 comprises 1.8 mol% methane, 50.8 mol% ethane and 47.4 mol% propane.
  • Table 2. Process conditions of streams in refrigerant cycle in a simulated example. Stream no.
  • Compressor arrangement of present invention Compressor arrangement consisting of 2 centrifugal compressors in series Energy added to refrigerant Total work of compressors 5 and 6 [MW] 87.6 90.8 Heat transferred from 14b [MW] 130.6 130.6 Heat transferred from 14a [MW] 49.9 49.9 Balance [MW] 268.1 271.3 Energy rejected by refrigerant Duty of heat exchanger 13 [MW] 268.1 271.3 Balance [MW] 0 0 CoP 2.06 1.99
  • stream 50 may be heat exchanged against another stream.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP06124522A 2005-11-24 2006-11-22 Procédé et dispositif de refroidissement d'un courant, en particulier d'un courant d'hydrocarbures comme du gaz naturel Withdrawn EP1790926A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05111197 2005-11-24

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EP1790926A1 true EP1790926A1 (fr) 2007-05-30

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US (1) US8181481B2 (fr)
EP (1) EP1790926A1 (fr)
JP (1) JP5097951B2 (fr)

Cited By (9)

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WO2008020044A3 (fr) * 2006-08-17 2008-11-27 Shell Int Research Procédé et appareil de liquéfaction d'un courant d'alimentation contenant des hydrocarbures
WO2009072900A1 (fr) * 2007-12-06 2009-06-11 Kanfa Aragon As Procédé et système permettant de réguler la capacité de refroidissement d'un système de refroidissement sur la base d'un processus d'expansion gazeuse
US8181481B2 (en) 2005-11-24 2012-05-22 Shell Oil Company Method and apparatus for cooling a stream, in particular a hydrocarbon stream such as natural gas
US9441877B2 (en) 2010-03-17 2016-09-13 Chart Inc. Integrated pre-cooled mixed refrigerant system and method
US9562717B2 (en) 2010-03-25 2017-02-07 The University Of Manchester Refrigeration process
US10480851B2 (en) 2013-03-15 2019-11-19 Chart Energy & Chemicals, Inc. Mixed refrigerant system and method
US10663221B2 (en) 2015-07-08 2020-05-26 Chart Energy & Chemicals, Inc. Mixed refrigerant system and method
US11408673B2 (en) 2013-03-15 2022-08-09 Chart Energy & Chemicals, Inc. Mixed refrigerant system and method
US11428463B2 (en) 2013-03-15 2022-08-30 Chart Energy & Chemicals, Inc. Mixed refrigerant system and method

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WO2008157757A1 (fr) * 2007-06-21 2008-12-24 E. I. Du Pont De Nemours And Company Procédé de détection de fuite dans un système de transport de chaleur
US8464551B2 (en) * 2008-11-18 2013-06-18 Air Products And Chemicals, Inc. Liquefaction method and system
DE102011015433A1 (de) * 2011-03-29 2012-10-04 Linde Ag Wärmetauschersystem
US10480852B2 (en) 2014-12-12 2019-11-19 Dresser-Rand Company System and method for liquefaction of natural gas

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